Governing system for rotating machines



March 2 1926. 1,575,158

1 w. B. FLANDERS GOVERNING SYSTEM FOR ROTATING MACHINES Filed July 12, 1921 2 Sheets-Sheet 1 a F N H 3 f a Q m u G i i Q N a a g a v Q 8 o u Q g N a 5+ J G i a Q a Q r ATTORNEY March 2 1926. 1,575,158

W. B. FLANDERS GOVERNING SYSTEM FOR ROTATING MACHINES Filed July 12, 1921 2 Sheets$heet 2 fiandezg INVENT ATTGNEY Patented Mar. 2, 1926.

UNITED STATES WARREN B. FLANDERS. OF PHILADELPHIA, PENNSYLVANIA, ASSIGNOR TO WEST- INGHOUSE ELECTRIC AND MANUFACTURING COMPANY, A CORPORATION PENNSYLVANIA.

GOVERNING SYSTEM FOR ROTATING MACHINES.

Application fled July 12, 1921.

To all whom it may concern:

Be it known that I, IVARREN B. FLANnEus, a citizen of the United States, and a resident of Philadelphia, in the county, of Philadelphia and State of Pennsylvania, have invented a new and useful Improvement in Governing Systems for Rotating Machines, of which the following is a specification.

My invention relates to governing mechanisms, more particularly of the hydraulic type, and has for its object to provide apparatus of the character designated which shall be simple in construction, reliable in operation, and which shall require but little attention while in operation.

In the drawings, attached hereto and forming a part of this application, Fig. 1 is a side elevation of a turbine showing my improved governing mechanism applied thereto; Figure 2 is a vertical sectional view of a portion of the governing mechanism; Fig. 3 is a detail sectional view of the hydraulic pressure-developing device; and Fig. 4 is a diagrammatic view of my improved hydraulic governing mechanism showing how it may be applied to a plurality of turbines; and Figure 5 is a detailed sectional view of a part of the mechanism.

, It is desirable to provide marine turbines with governing devices in order to properly regulate the speed thereof, particularly if a ship encounters a rough or stormy sea. Heretofore, governing mechanisms have been employed in situations of this kind which utilize steam relays between the governors and the motive fluid admission valves; however, a steam-relay is likely to become salted or rusted, thereby preventing the pro er operation of the mechanism when caller upon,

and this undesirable result is very likely to occur at sea for the reason that the turbine or turbines of a ship may run for long periods under substantially constant loads and, consequently, the various relatively movable parts of the governing mechanism may occupy substantially the same positions for long periods, thereby, at times, permit ting salt and rust to freeze the parts together and prevent proper operation.

In accordance with my present invention I provide a hydraulic governing mechanism for the motive fluid admission valve of a prime mover of the character described which shall not be subject to the objections Serial No. 484,100.

provide an autostop overnor together with means actuated there y upon an overspeed of the prime mover for closing the governor controlled admission valve.

Referring now more particularly to the drawings for a detailed description of my invention, I show a prime mover, for example a steam turbine 10. provided with a suitable steam inlet 11, having an admission valve at 12, which is under the control of the governor mechanism, to be described.

e governor mechanism comprises a means for supplying oil under pressure in accordance wlth the speed of the turbine, an oil relay mechanism which utilizes the ressure of the oil to move the motive fiui admission valve 12, and a pressure-responsive device which is responsive to the pressure of the oil to control the operation of therelay.

The means for maintaining a supply of oil whose pressure varies with the speedof the turbine, preferably comprises a pump including a suitable impeller 15 arranged within a casing 17, the impeller being secured to a suitable shaft or rotatatle element 16 of the turbine. The casing 17 is provided with an oil outlet conduit 18 and oil inlet conduits 19 and 20. As shown in Fig. 3, the

casing 17 is provided with an interior partition 21, which divides it into a pain chamber and an oil supply or collecting c amber communicating therewith. Theimpeller acts on the oil in the pump chamber to force it out and through the outlet conduit 18. It will be obvious that the pressure of oil in the conduit 18 will vary as the square of the velocity of the turbine. As may be seen from Figs. 1 and 4, the conduit 18 is provided with a branch 22 communicating with the oil relay and a branch 22' communicating with the pressure-responsive device.

The oil relay comprises a double-acting motor device, which is connected to the motive fluid admission valve 12 for the purpose of moving the latter to vary the uantity of motive fluid admitted to the turbine, and the operation of the motor deviceis controlled by a suitable pilot valve which is initially moved by the pressure-responsive device. 7

The motor device comprises an operatin cylinder 23 having a piston 24 arranged therein and connected to piston rod structure, including a suitable rod 25 and an upper enlarged cylindrical portion 26 connected thereto. The piston rod structure is pivotally connected, at 27, to one end of the lever 28, fulcrumed at 29 to a suitable supporting link 30, the other end of the lever being pivotally connected, at 31, to the stem 32 of the valve 12.

Oil, under pressure, is admitted to either end of the operating cylinder 23 and exhaustcd from the other end to secure actuation of the piston 24 in the manner stated. For this purpose, the cylinder structure 23 is provided with suitable inlet and exhaust ports 33 and 34 under control of a pilot valve, to be described.

The pilot valve comprises a suitable housing 36 having a central port or chamber 37, adapted for communication with the branch conduit 22, suitable chambers or passages 38 and 39 communicating with the ports 33 and 34, respectively, and end chambers or passages 40 and 41 communicating with the conduit 19 for the purpose of conducting exhaust from the operating cylinder of the motor device back to the casing 17 of the impeller pump. The valve housing 36 is pref erably' provided with bushings having ports communicating with the chambers or pas sages 38, 39, 40, and 41 and which are spaped apart sufliciently to afford communication with the central chamber 37. The bushings, together, define piston valve cylinders for the piston valve 45, which is provided with a plurality of piston portions 46 cooperating, with the central chamber 37, the ports 38 and 39, and the end ports 40 and 41, to supply oil under pressure to either end of the operating cylinder 23 and to exhaust oil therefrom. The piston valve is preferably provided with a collar or shoulder 17 for the purpose of limiting the travel thereof to the proper and required amount. The piston valve is pivotally connected, at 48, to a link 49 which pivotally connects, at 50, with a floating lever 51, which, at one end, is pivotally connected at 52 with the cylindrical portion 26 of the piston rod structure of the operating piston 24, and, at the other end. is pivotally connected, at 53, to the angular portion 54 of the lever 56, which is fulcrumed at 57 on a standard 58 the latter also serving as a guide for the portion 26 of the piston rod structure, and the other end of the lever 56 is connected to a pressure-responsive device.

The ressu're-responsive device comprises a cylin er 60, a piston 61 therein, and a rod 62.which is operatively connected by means of a double lever or yoke connection to one end of the lever 56. The piston 61 is biased toward the lower end of the cylinder 60 by means of a. suitable adjustable spring 65, the latter hearing, at its lower end, upon the upper face of the piston 61 and having its upper end carried by an adjustable abutment 66 which is threaded with relation to the upper closure portion 67 of the cylinder 60 and has one end extending above the cover, whereby the abutment is readily accessible to vary the tension of the spring 65. The lower side of the piston 61 is acted upon by the pressure of oil received from the branch conduit 22'. which communicates with the supply conduit 18 of the impeller pump.

lh'cferably, the piston 61 is so related to the cylinder. to the piston rod 62. and to the spring 65. that it is capable of moving freely. \crordingly, the lower portion of the cylinder 66 is provided with a head 6!), adapted to be secured thereto in any suitable manner. and provided with a central upstanding boss or cylindrical portion 70 which is provided with an interior port or passage 71 communicating with the conduit 22' aforesaid. The upstanding boss or cylindrical portion 70 serves as a guide for the cylindrical portion 72 of the piston61. In order to prevent the spring 65 from cxerting any side pressure on the piston, the lower end thereof is preferably supported on the piston by means of a pair of gimbal rings 73 and 74, the lower of which is supported by the piston. The upper end of the cylindrical portion 72 of the piston is provided with a. socket member 75 to receive the ball portion 76 carried by the lower portion of the rod 62. From the structure described, it will be apparent that neither the spring 65 nor the rod 62 serves to interfere glith the ready reciprocation of the piston The cylinder 60 is provided with a suitable leak-oil conduit 77 arranged above the. piston. Oil, under pressure, enters the cylinder, beneath the piston 61, and causes the latter to. move upwardly until the pressure exerted by the spring is equal to that of the oil. At the same time, oil may escape around the edges of the piston 61 and be di charged through the leak-oil conduit 77 which communicates with a suitable sump. From the structure so far described, and with particular reference to diagrammatic view, Fig. 4, the operation of my governing mechanism will be readily understood. The impeller 15 carried by the turbine shaft 16 develops pressure of oil which varies as the square of the velocity of the impeller. As already stated, the outlet conduit 18 communicates both with the pressure-responsive device and with the valve chamber of the motor device. Upon the turbine speeding up, the pressure of oil in the conduit 18 accordingly rises and acts upon the lower face of the piston 61 of the pressure-responsive device to move the piston upwardly. Vixen the piston moves up, the rod 62 causes the lever 56 to move about its fulcrum 57 to move the lever 51 downwardly about the pivotal connection 52, as a fulcrum, resulting in downward movement of the piston valve 45 and the establishment of communication between the central pressure chambar 37 and the lower port or passage 34 to supply oil under pressure below the piston 24 to move the latter upwardly to rock the lever 28 about its fulcrum 29 and move the admission valve 12 towards closing position in order to restrict the supply of motlve fluid to the turbine. At the same time that comnmnication is established between the pressure-supply main 22 and the lower portion of the cylinder 23 beneath the piston 24, the space above the piston is connected to the upper end chamber or passage 40, whereby the oil in the upper portion of the cylinder may be exhausted. When the prime mover or turbine drops in speed below a desired amount, the converse operation takes place and the piston of the motor device moves downwardly in order to open wider the motive fluid admission valve in order to admit more fluid. Whenever the piston valve 45 is moved by the pressure-responsive device, it will be obvious that it will be brought back to a median position, as one end of the floating lever 51 is pivotally connected at 53 to the piston structure of the motor device.

A suitable auto-stop mechanism is associated with the governing mechanism in order to quickly close the motive fluid admission valve, should the speed of the turbine exceed a predetermined amount. For this purpose, I have provided an auto-stop cylinder 80 having a piston 81 therein whic has a lost-motion connection with a depending link 82 carried by a yoke 82', the latter being connected to one end of the lever 56 by pivot means 55. The upper end of. the cylinder 80 has a live steam inlet 83 and a steam outlet '84, the latter being connected by means of the conduit 85 with the autostop valve and trigger mechanism 86, shown more in detail in Fig. 3. The conduit 85 is adapted to communicate with a chamber normally closed by means of a valve 87, held in closed position by means of a well-known lever 88 and trigger device 89, cooperating therewith. One end of the trigger or trip lever is arranged contiguously to an eccentrically weighted turbine shaft, an which is ada ted to fly out, upon the attainment of a predetermined speed, to trip the trigger or latch lever 89, thereby permitting the lever 88 to tilt and the valve 87 to open. As soon as the valve 87 opens, the steam pressure below the pie ton 81 drops and the piston is caused to move quickly to the bottom of the cylinder 80, due to the pressure of live steam above the'piston. When the piston 81 moves down, in

(portion 90, carried by the the manner stated, it pulls down on the link 82 and causes the floating lever 51 to fulcrum about the pivotal connection 50, the piston valve 45 moving downwardly until the stop collar 47 limits further movement, in order to quickly move the member 26 upwardly to close the motive fluid inlet valve. As the piston valve 45 is in its lowermost position, communication is established between the portion of the cylinder 23 above the piston 24 and the exhaust and between the pressure supply port 37 and the space below the piston. Under these conditions, the member 26, attached to the piston 24, moves upwardly both in response to the movement of the piston 81 and the admission of fluid under pressure beneath the piston 24. In some cases it may happen that the oil pressure for actuating the piston 24 inay fail; however, with my improved type of apparatus, the admission of steam to the turbine would be cut off, due to the movement of the auto-stop piston 81 acting through the rod 82, the yoke 82', the pivotal connection 55, the angular portion 54 of the lever 56, and the floating lever 51, the latter fulcruming first about the pivotal connection 52 to move the piston valve 45 to its lowermost position and then fulcruming about the ivotal connection 50 with respect to the link 49, connected to the piston valve 45, when the pis- -ton valve comes to a stop in its lowermost position, to move the member 26 upwardly, thereby rocking the lever 28 to close the admission valve 12, the proliminary downward movement of the piston valve 45 afi'ording communication of the space above the piston 24 with the exhaust so as to permit upward movement of the member 26 and the piston 24. Upon resetting the lever 88 and the latch 89, the valve 87 is closed and steam escaping by the piston 81 quickly builds up the pressure beneath the piston so that the differential effect of the piston results in the movement thereof to its upper normal position.

It'will be obvious that the moving of the piston 61 of-the pressure-responsive device should not be interfered with by the auto= stop piston 81; and, on the other hand, the pressure-responsive device should not interfere with the ready movement of the autostop piston. I have, therefore, provided a Vieldable abutment connection 95 between" the left hand end of the lever 56 and the upper end of the rod 62. This connection comprises abutments 96 and 97, carried by the rod 62 and the lever 56, respectively. A spring 98 is arranged between the abutments. Obviously, then. upon movement of the auto-stop piston 81 downwardly, the lever 56 may readily move about its fulcrum connection 62 without lifting the piston 61, the movement of the lever 56 taking place with a mere movement of the abutment 97 III toward the abutment 90 and a compression of the spring 08.

In order to permit of the ready movement of the piston 1 and the associated linkage without being opposed by the piston of the auto-stop device, a lost-motion connection is provided between the piston 81 and the link 82 so that the latter may readily move downwardly with respect to the piston without being opposed by or moving the piston. Preferably, the piston is provided with a hollow stem which extends beyond the autostop cylinder and provides for, not only the differential pressure effect to keep the piston in its upper normal position, but also for the lost motion connection. The. hollow stem portion of the piston 81 is provided with an inwardly projecting shoulder 100 which cooperates with a head 101. carried by the lower end of the link S2. structure described, it will be apparent that, when the pressure-responsive device moves and results in action of the operating cylinder, to effect movement of the motive fluid admission valve, the auto-stop piston offers no resistance. However, upon the turbine exceeding a predetermined speed, the autos'top piston 81 moves downwardly quickly, the shoulder 100 coming in contact with the head 101 and pulling the link 82 downwardl v, which causes the floating lever 51 to fulcrum about the pivotal connection 50 and the piston rod 25 of the motor device to move upwardly, resulting in a tilting of the lever 28 about its fulcrum connection 20 to close the fluid admission valve 12. As already stated, before the floating lever 51 begins to fulcrum about the pivotal connection 50, the piston valve 45 is moved to its lowermost position, whereupon the piston 81 acts through the rod 82, the yoke 82', the pivotal connection 55. the angular portion 54 of the lever 50, and the floating lever 51, the latter fulcruming about the pivotal connection 50, to move the member 20 upwardly so as to tilt the lever 28 about its fulcrum 20 to close the fluid-arhnission valve 12. The piston 81 is assisted in the closure of the admission valve by the admission of fluid under pressure beneath the piston 24. \Vhen the piston valve 45 is moved to its lowermost position, the space above the piston 24 is placed in communication with the exhaust and the space below the piston 2t is placed in communication with the supply of fluid under pressure. Therefore, when the auto-stop mechanism operates, the piston 81 moves downwardly, preliminarily moving the piston valve 45 downwardly, so as to place the space above the piston 24 in communication with the exhaust and the space below the piston 24 in communication with the supply fluid under pressure, so that the admission valve 12 is quickly moved toward From the.

its cut-off position, due to the agency of the downwardly moving piston 81, assisted by the. fluid under pressure acting beneath the piston 24. As already stated, if the pressure of fluid should fail, the piston 81 is effective by itself to close the admission valve 12.

As shown in Figure 1, appropriate leakofi' connections 105, 106, and 107 are associated, respectively, with the gland member for the piston rod 25 and with the glands or-packing devices associated with the upper and lower ends of the piston valve 43. 'l'hese leak-off connections may be connected to a conduit 108 which may connect with the leak-off conduit 77, aforesaid, adapted for, connecting to an appropriate sump.

\Vhcn the turbine is started. of course, no pressure exists in the system, and it is necessary to supply initial pressure to the pressure-responsive device, and to the operating cylinder of the relay to secure an opening of the motive fluid admission valve. Accordingly, in Figs. 1 and 4, I show an auxiliary connection 110 which communicates with a suitable supply of oil, under pressure, for example, the bearing supply. The connection 110 is provided with one or more checkalves 111, in order to prevent back flow through the conduit, and the conduit 18 is provided with a check valve 112 in order to prevent oil under pressure from the auxiliary or bearing supply from flowing back into the impeller pump. It will be obvious, therefore, that, upon starting, oil under pressure is admitted from the auxiliary source of supply which results in an upward move ment of the piston 61 of the pressure-responsive device and a downward movement of the piston 24 of the motor motive fluid admission valve 12. As soon as the turbine starts, the impeller 15 builds up pressure in the conduit 18, and the connection 110 from the auxiliary supply may then be closed.

In order to prevent the piston having a hunting effect, due tuations in the pressure 01 from to possible fineof oil supplied thereto, an appropriate check valve 113 is provided which opens in the direction of the pressure-responsive device. It will, therefore, be apparent that the pressure below the piston 01 will not behave in an erratic manner, but will accelerate or decelerategradually. In this connection, as already stated, the piston has a loose fit with respect to its cylinder 60 so as to permit the ready dissipation of oil pressure beneath the piston upon a drop in pressure in the conduits 18, 22 and 22, thereby rendering possible the ready movement of the piston 61 downwarcly under the influence of the spring to so move the pilot valve as to secure opening of the motive fluid admission valve device to open the ill) V device to supply an increased of the motive fluid inlet valve.

to a wider position by means of the motor quantity of motive fluid to the turbine. 7

With turbines of the character indicated, thrust bearings are ordinarily provided which are copiously supplied with oil. I, therefore, propose to utilize the over-flow of oil from a thrust bearing to serve as the make-u supply for the impeller amp. I have, t erefore, shown the conduit 20, in Fig. 1, communicating with the upper portion of the thrust bearing casing 115.

In order to secure pro er balance of the linkage associated with t e pistons and the motive fluid inlet valve, suitable adjustable wei hts-116 may be provided in connection witli one of the elements of the linkage, for erample', the lever 56.

From the above, it will be seen that the impeller pump develops oil pressure which varies with the velocity ofthe turbine, supplyin oil under pressure, in the manner state to the pressure-responsive device and to the oil relay to secure proper actuation Exhaust from the operating cylinder of the motor device flows back through the conduit 19 and enters "the casing of the impeller pump.

- Leakage around the piston of the pressurefires onsive device, from around the piston re 25, and from around the ends of the piston valve 15, is collected in the manner set forth and conducted to an appro riate sump. Oil, to make u for the losses ue to leakage, is supplied from the over-flow of the thrust bearing casing 115 by means ofa conduit 20 to the casing of the impeller pump. It will, therefore, be seen, that I have provided 'a very compact governin which incidentally involves a In ricating medium as its actuating agent, and which is notsubject to the objection of freezing up, due to salt and rust, as has been the case, at times, with the steam relay type of govern- :ing mechanism.

Asmay be seen from Figure 4 my type of governin mechanism is readily susceptible of application to a plurality of turbine units having a common steam inlet under the control of an admission valve 12. In this case, each of the turbine spindles or shafts 16 would have secured thereto, impellers 15 arranged within the impeller caslugs 17 to supply oil under pressure through the conduits 18 to the pressure-responsive and relay devices. Check valves 117 are provided in the conduits 18 associated with the impeller pumps in order to prevent flow from one pump to the other when one turbine isshut down.

It will be readily apparentjhat the gov-' erning mechanism may be easily tested merely by pushing down on the right-hand side of the lever 56. This will result in a temporary cutting-down cf the steam Supsystemply, but the apparatus will rapidly regain its normal position.

From the foregoing,- it will be seen that I have devised a governing mechanism which utilizes oil under pressure to secure actuation of the relay instead of the movement of governor weights for this purpose. Hence, my governing mechanism is a self-contained and unexposed unit having all those parts which would ordinarily be subject to being rusted or salted, resulting in disabling of the apparatus, exposed to oil, whereby the governing device may be maintained in good condition with a minimum amount of attention.

As already pointed out, the impeller 15 of the pumping device develops pressureof fluid w ich varies as the square of the speed thereof. Since the pressure responsive device, includi thevpiston Gland the cylinder 60, and there ay or motor device, including the cylinder 23 and; the piston 24, involve more or less displacement in operation, it is essential to use a pump of t e pressure type instead of one of the displacement type for the reason that the pressure of a pump of the latter type is secured by positive flow due to the displacing element; and, therefore, if a pump of the dis lacement ty e should be associated with d isplaceable e ements, such as the pistonsfof the pressureresponsive device and the relay, as soon as these elements should start to move the pressure of the system would immediately be relieved, thereby making it impossible to secure immediate movement of the admission valve 12 in response to pressure changes in thesystem. As Iutilize-a pumping device of'the impeller type'which develops" pressure by imparting velocity to the'fluid articles cast oil from the impeller, it will e evident that pressure is maintained in the fluid system connected to the pressure responsive device and to the relay regardless of whether or not any fluid is flowing or of the 'rateof flow. A pump having the characteristic of maintaining ressure regardless of flow conditions is, 't erefore, es-

sential to my fluid governing mechanism; I,

therefore, desire it to be'understood that the term impeller is used to designate any type of pump rotor or runner whose first effect is to impart velocity to fluid and which is capable of maintaining a pressure which varies as the square of-the speed regardless of the rate of discharge of fluid.

\Vhile I have shown my invention in but one form, it will be obvious to those skilled in the art that it is not so limited but is sus oeptible of various other changes and modifications without departing from the spirit thereof, and I desire, therefore, that only such limitations shall be placed thereupon as are imposed by the prior art or as are specifically set forth in 'the appended claims.

\Vhat I claim is 1. In combination, with a prime mover oil relay valve operating mechanism having a pilot valve and an operatin cylinder not its piston member, connected to a motive fluid admission valve, in device responsive to fluid pressure connected to the'pilot valve for actuating the latter, and an auto-stop mechanism connected to the piston member for actuating the latter to close the admission valve upon overspeeding of the prime mover.

2. In combination, with a prime mover oil relay valve operating mechanism havin a. pilot valve and an operating cylinder wit 1 its piston structure, a pressure-responsive device, a linkage connection between the pressure;respons1ve device and the pilot valve, an auto-stop mechanism, and a linkage vconnection between the auto-stop mech anism and the piston structure of said operating cylinder including a lost-motion connection.

3. In combination, with an elastiofluid turbine having an elastic-fluid admission valve, an oil relay having an operating piston connected to the admission valve by a linkage connection and a valve for control ling the operation of the operating piston, a pressure-responsive device, a linkage connection between the pressureresponsive device and said COIliLlOlllll valve, an auto-stop mechanism, and a lll1 3- 0 connection between the auto stop mec ianism and said operating piston, the linkage connection between the operating piston and the valve and between the auto-stop mechanism and the operating iston including lost-motion connections, wiereby the pressure-responsive device may. readily operate the controlling'valvc to secure operation of the operating piston and the auto-stop mechanism nmvreadily operate the operating piston to close the elastic tin-id admission valve.

4. In combination, with a turbine having a valve and auto-trip mechanism, a fluidpressure system in which the pressure of fluid varies with the speed of the turbine, a

motor device for moving the valve either in an opening -or a closing direction, a meclianism responsive to the pressure of said system to control the operation of the motor device,'and a connection between the autotrip mechanism and an element of said motor device to close the valve upon overspeeds.

5. The combination with an elastic fluid turbine having an admission valve, of an element movable in response to the speed of the turbine, a fluid pressure operated relay for transmitting movements of the element and controlling the admission valve, :1 device responsive to a definite overs eed of the tur ine, a second device actuate by the elastic lIlOtlVCfillld operatively connected to the fluid pressure operated rela and adapted to actuate said relay indepen ently of the element, and an operative connection between the device responsive to overspecd and said second device or controlling said second device, wherebyupon a definite overspeed of the prime mover, said second device operates toclose the admission valve.

6. The combination with an elastic fluid turbine having an admission valve, of an element movable in response to normal variations in the speed of the turbine, a fluid pressure operated relay for transmitting movements of the element and controlling the admission valve, :1 device responsive to a definite overspeed of the turbine, 21 second device actuated by the elastic motive fluid operatively connected to the fluid pres sure operated relay'and ada ted to actuate said relay independently of t e element and to close the admission valve, and an operative connection between the device responsive to oven-speed and said second device for controlling said second device, whereby upon a definite overspeed of the prime mover, said second device operates toclose the admis sion valve.

In testimony whereof, I have hereunto subscribed my name this eleventh day of July, .1921.

WARREN B; FLANDER-S.

\Vhat I claim is 1. In combination, with a prime mover oil relay valve operating mechanism havrn a pilot valve and an operating cylinder wit its )lStOIl member, connecte to a motive fluid admission valve, a device responsive to fluid pressure connected to the'pllot valve for actuating the latter, and an auto-stop mechanism connected to the piston member for actuating the latter to close the admission valve upon overspeeding of the prime mover.

2. In combination, with a prime mover oil relay valve operating mechanism havin a pilot valve and an operating cylinder w t 1 its piston structure, a pressure-responsive device, a linkage connection between the pressure -responsive device 0 and the 110i; valve, an auto-stop mechanism, and a inkage connection between the auto-stop mech anism and the piston Structure of said operating cylinder including a lost-motion connection.

3. In combination, with an elastic-fluid turbine having an elastic-fluid admission valve, an oil relay having an operating piston connected to the admission valve by a linkage connection and a valve for controlling the operation of the operating piston, a pressure-responsive device, a linkage connection between the pressure-responsive device and said COIltlOlllIl" valve, an auto-stop mechanism, and a 1in age connection between the auto-stop mechanism and said operating piston, the linkage connection between the operating piston and the valve and between the auto-stop mechanism and the operating piston including lost-motion connections, whereby the pressure-responsive device may. readily operate the controlling'va-lve to secure operation of the operating piston and the auto-stop mechanism may readily operate the operating piston to close the elastic fluid admission valve.

4. In combination, with a turbine havin a valve and auto-trip mechanism, a flui pressure system in which the pressure of fluid varies with the speed of the turbine, a

motor device for moving the valve either in an opening -or a closing direction, a mecli anisin responsive to the pressure of said system to control the operation of the motor device,'and a connection between the autotrip mechanism and an element of said motor device to close the valve u on overspeeds.

5. The combination with an elastic .fluid turbine havin an admission valve, of an element movalile in response to the speed of the turbine, a fluid pressure operated relay for transmitting movements of the element and controlling the admission valve, a device res onsive to a definite overs eed of the tur ine, a second device actuateci by the elastic motive fluid operatively connected to the fluid pressure operated rela and ada ted to actuate said relay indepen ently of t 1e element, and an operative connection between the device responsive to overspeed and said second device or controlling said second device, whereby upon a definite overspeed of the prime mover, said second device operates to close the admission valve.

6. The combination with an elastic fluid turbine having an admission valve, of an element movable in response to normal \ariations in the speed of the turbine, a fluid pressure operated relay for transmitting movements of the element and controlling the admission valve, 8. device responsive to a definite over-speed of the turbine, a second device actuated by the elastic motive fluid operatively connected to the fluid pressure operated relay and ads ted to actuate said relay independently of t e element and to close the admission valve, and an operative connection between the device responsive to overspeed and said second device for controlling said second device, whereby upon a definite overspeed of the prime mover, said second device operates toclose the admis sion valve.

In testimony whereof, I have hereunto subscribed my name this eleventh day of July, 1921. v

WARREN B. FLANDERS.

Certificate of Correction.

It is hereby certified that in Letters Patent No. 1 575,158, upon theapplication of,Warren B. Flanders of i an improvement in Governing Systems for 1i in the rinted specification requiring correction as fo lows: 6, line 58, after the word to insert the words normal variations m; and that the said amed March a, 1920, hiladeclfii 'a, Pennsylvama, ,for

Ma ines, an error appears otat-in Letters Patent should be read with this correction therein that the same may conform to the record of the case in the Patent Oflice.

Signed and sealed his 18th day of May, A. D. 1926.

M. J. MOORE,

Acting Ganwzim'mr of Patents.

Certificate of Correction.

It is hereby certified that in Letters Patent No. 1,575,158, anted March 2, 1926, upon the application of Warren B. Flanders, of Philadelp a, Pennsylvania for an improvement in Governing Systems for Rotating Machines, an error a pears in the printed specification requiring correction as follows: Page 6, line 58, c aim 5,

after the Word to insert the words normal variations in; and that the said Letters Patent should be read with this correction therein that the same may conform to the record of the case in the Patent Ofiice.

Signed and sealed his 18th day of May, A. D. 1926.

[m] M. J. MOORE,

Acting Oommziasz'mwr of Patents. 

